Hydrodynamic torque converter

ABSTRACT

The invention relates to a hydrodynamic torque converter having an impeller wheel, a turbine wheel and an oscillation damper which is accommodated in the converter housing, and a converter lockup clutch. Two damper stages are arranged here as a serial damper between the output hub of the torque converter and the converter lockup clutch, and a damper stage is arranged between the turbine wheel and the output hub. In order to improve the damping properties, a rotary oscillation absorber is additionally provided which is arranged between the dampers and is also connected to the turbine wheel in a rotationally fixed fashion.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a reissue of U.S. Pat. No. 8,573,374, issued Nov. 5,2013, which is hereby incorporated by reference herein. U.S. Pat. No.8,573,374 was issued from U.S. application Ser. No. 13/000,076, which isthe National Stage of PCT International Application No.PCT/DE2009/000819, filed Jun. 12, 2009, which application published inGerman and is hereby incorporated by reference in its entirety, whichapplication claims priority from German Patent Application No. DE 102008 031 431.5, filed Jul. 4, 2008 and from German Patent ApplicationNo. DE 10 2008 037 808.9, filed Aug. 14, 2008 which applications areincorporated by reference in their entirety.

FIELD OF THE INVENTION

The invention relates to a hydrodynamic torque converter with a lock-upclutch and a multistage torsional vibration damper.

BACKGROUND OF THE INVENTION

Such torque converters are particularly used in vehicle drive trains,between an internal combustion engine and transmission. To damptorsional vibrations of an internal combustion engine, the so-calledtorsional vibration dampers are used, which are driven via an inputpart, whereby the torque is transmitted to an output part that isrelatively and limitedly rotatable with respect to said part, andthrough compression of energy accumulators, the energy is temporarilystored at torque peaks and released to the output part at torquetroughs. The torque converter is configured by means of a dampingdevice, a so-called conventional damper between the lock-up clutch andthe output hub of the torque converter so that when the lock-up clutchis closed, torsional vibrations are damped via the torque path betweenconverter housing and output hub. Furthermore, the so-called turbinedampers are known which by open or missing lock-up clutch, after initialhydraulic damping between impeller and turbine, still damp the remainingtorsional vibrations and as such are disposed between the turbine andoutput hub. Furthermore, combinations of both damper types are known.

Another form of reducing torsional vibrations is the absorber principleby which movable masses are disposed on mounting parts to counteract theeffect of energy accumulators or in the case of centrifugal forcependulums, absorber masses are disposed tiltably on raceways extendingin circumferential- and radially direction and hence the inertial momentof the mounting part is varied depending on vibration influences.

Just as more restrictive assembly space specifications in motorvehicles, especially in transverse drive units comprising internalcombustion engine and transmission as well as the torque converterdisposed in between, also the assembly space requirement for theembodiment of torque converters increases if sufficient vibrationdamping is sought. Task of the invention is therefore furtherdevelopment of a torque converter with little assembly space butsufficient vibration damping.

BRIEF SUMMARY OF THE INVENTION

The task is solved by means of a hydrodynamic torque converter with aturbine driven by an impeller as well as housing in which a torsionalvibration damper with multiple damper stages and a torsional vibrationabsorber and a lockup clutch are additionally mounted, whereby twodamper stages are disposed in series between the lock-up clutch and anoutput hub, the torsional vibration absorber between the damper stages,and a damper stage between the turbine and output hub, whereby thetorsional vibration absorber is connected non-rotatably with theturbine. Through the proposed disposition, a torsional vibrationabsorber, for instance a centrifugal force pendulum, can be providedwith both damper stages, so that the damper stages in overall can bedesigned for a smaller assembly space. A further advantage is thepartition of the torsional vibration dampers in at least two damperstages, whereby the torsional vibration damper exercises two functions,namely that of a series damper and the other of a turbine damper.Through integration of both damper stages in a single damper thatconcurrently features a torsional vibration absorber assigned to bothdamper stages, multiple components can be shared, so that in overall,for a given assembly space and damping capacity, a lighter and narrowertorque converter can be proposed. For torque increase, particularly at alow speed range, a stator with one way clutch can be disposed moreovernon-rotatably fixed in housing between impeller and turbine.

The common inventive concept comprises a multiple number of additionalmeasures that can be combined or used individually in order to obtain anarrower assembly space. For instance, an input part of the first damperstage and an output part of the second damper stage can be centered onone another, so that, on the same axial assembly space, an input partand an output part can be mounted. Both components are thereby supportedrotatably relative to one another. For instance, an output part of thesecond damper stage can be disposed radially within the first damperstage.

Furthermore, several components of different damper stages with respectto their function can be formed as one piece. For instance, at least adisk part can be formed as one piece out of an in input- and an outputpart of two damper stages. For example, an output part of a radial,outer damper stage can at the same time form a centrifugal forcesupport, in that the disk part is guided accordingly radially outside,at least partially around the energy accumulators. Window cutouts forreceiving the energy accumulators can be provided radially inside.Furthermore, such a formed disk part can form the turbine hub or theturbine shell can at least be mounted on said disk part, for instanceriveted. This disk part can be mounted rotatably radially inside, on theoutput hub, so that with a flange part of the output hub byinterposition of energy accumulators acting in circumferentialdirection, the second damper stage can be formed as turbine damper.

The torsional vibration absorber is preferably formed as a centrifugalforce pendulum, whereby a mounting part accommodating absorber massesdistributed over the circumference of the torsional vibration absorberand a disk part of the input part of a damper stage can be formed as onepiece. Thereby, a two-part input part, for instance, of the seconddamper stage can be formed of two axially spaced disk parts, whereby thefirst disk part concurrently entails the mounting part and the seconddisk part is formed as one piece with the output part of the firstdamper stage. The disk part not containing the mounting part isconnected non-rotatably, for linking the torsional vibration absorber tothe first damper stage, with the other disk part by means of fasteningmeans like rivets.

To minimize axial assembly space, components can be disposed axiallyover-lapping, in that they are radially disposed where the othercomponent features a radial slit or design. For instance, absorbermasses of the torsional vibration absorber and energy accumulators ofthe first damper stage disposed over the circumference can be disposedat the same height radially and axially spaced from one another, wherebya middle mounting diameter of the energy accumulators is disposedradially outside the turbine. In this manner, the energy accumulatorscan at least partially axially overlap the turbine, for instance, on itstorus tapering on the external circumference.

Furthermore, the energy accumulators can be distributed over thecircumference of the second damper stage, based on a middle mountingdiameter, radially within the turbine blades. The energy accumulators ofthe second damper stage can thereby particularly through the torus formof the turbines be brought so close to the turbine shell so that radialouter areas of the turbines and the axial edge areas of the energyaccumulators intersect axially. Altogether, the torsional vibrationdamper can therefore be brought close to the turbine, so that the end ofthe torsional vibration damper towards the lock-up clutch is essentiallyflat and the lock-up clutch can be closer to the torsional vibrationdamper.

For further reduction of the axial assembly space, the lock-up clutch inclosed state can be disposed axially in a fastening means providedradially within the outside part of the torque converter mounted in apocket formed on the housing wall. In this manner, the torque convertercan be disposed closely on a flex plate or a drive plate, whereby aradially disposed constriction, about the rotation axis, of theconverter housing can provide axial assembly space for the crankshaftwith a mounting for the flex plate.

The lock-up clutch furthermore can be disposed radially within theabsorber masses. To increase the capacity of the torque capable of beingtransmitted by such reduced friction diameter, the lock-up clutch can beequipped with a friction plate that is pressurized by a piston centeredon the output hub and that is axially displaceable on the housing andnon-rotatably mounted axially opposite the converter housing forming africtional closure.

The mounting part for absorber masses can be disposed axially betweenthe lock-up clutch and the first damper stage. For the transmission oftorque from the lock-up clutch to the first damper stage are transitiontransmission connections provided between the lock-up clutch and theinput part of the first damper stage, which are guided through themounting part. To allow rotational clearance between the fixed mountingpart on output side and the input part of the first damper stage, thecircular segment-shaped openings are provided in the mounting part.Moreover, the passage openings serve as limit stops and when rotaryclearance is used up, they transmit torque further to the first damperstage and directly via transmission connections into the second damperstage.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

The invention is illustrated in detail based on the exemplary embodimentshown in the only FIGURE. This FIGURE shows a hydrodynamic torqueconverter disposed about a rotation axis in a half-sectional view.

The FIGURE shows the hydrodynamic torque converter 1 in half-sectionalview above the rotation axis 2. The housing 3 is formed out of thehousing parts 4, 5, which are welded with one another after installationof internal parts. The impeller 6 is integrated inside the housing part4, so that upon rotation of the housing 3 the turbine 7 with turbineblades 8 is driven by converter fluid inside the housing 3. The housing3 is driven by an internal combustion engine—not depicted. For thispurpose, fastening means 9 attached to the housing part 5, for instancewelded with a rigid drive- or flex plate preferably axially elastic butrigid in circumferential direction, are rigidly connected with thecrankshaft of the internal combustion engine, with the housing 3 afterjoining the torque converter mounted on the transmission and rigidlyconnected e.g. screwed with the internal combustion engine. A stator 10is connected e.g. splined between an impeller 6 and turbine 7 viaone-way clutch 11 with a transmission stub—not depicted.

The output part of the torque converter 1 is formed by the output hub12, which is connected e.g. splined non-rotatably with a transmissioninput shaft—not depicted. A lock-up clutch 13 is mounted inside thehousing 3, which in the closed state transmits the torque from theinternal combustion engine to the housing 3 via the damper stages 14, 15into the output hub 12. When the lock-up clutch 13 is open, torque flowsvia the impeller 6 to the turbine and from there via the damper stage 15into the output hub 12. For a slipping lockup clutch 13 partial torquecan be transmitted via both torque paths.

The lock-up clutch 13 is formed by a piston 18 rotatably mounted on theoutput hub 12, axially displaceable and sealed, which is connectednon-rotatably with the housing by means of leaf springs 19. By adjustinga differential pressure between the two chambers 20, 21, piston 18adjusts an axial force between itself and a housing wall 23, so that africtional lock forms on the interposed friction plate 22 and thefriction surfaces of the piston 18 and housing wall 23. The housing wall23 is formed as an annular pocket 24 in which the piston 18 and thefriction plate 22 are fully received axially when the lock-up clutch 13is closed. Through formation of the lock-up clutch 13 with a two-sidedfriction plate, the latter can for the same torque capable of beingtransmitted be mounted on a diameter that radially lies within thefastening means 9, so that an accommodation neutral to the assemblyspace of the lock-up clutch 13 is necessary with respect of the axialassembly. The fastening means 9 can therefore be displaced axiallytowards the transmission for a specified radial diameter throughtapering of the housing part 5, so that the connection to the flex platecan occur by reducing an axial distance apart.

The torsional vibration damper 16 with the damper stages 14, 15 isdesigned as a multi-function damper. The two damper stages 14, 15 areconnected with one another by a single-piece disk part 25 assigned tothe damper stages 14, 15, which is centered rotatably radially inside onthe output hub 12. Radially outside is the turbine shell of the turbine7 connected with the disk part 25 by fastening means 26 e.g. rivets.Radially outside the fastening means 26, for instance, the energyaccumulators 27, of the damper stage 15, formed as coil springsdistributed over the circumference, are mounted in window-shapedrecesses 28, which support the energy accumulators throughcorrespondingly formed-parts against the centrifugal force effect. Onthe external circumference of the disk part 25 are energy accumulators29 of the damper stage 14 mounted and supported against centrifugalforce. For this, the disk part 25 features formed-parts 30, whichsurround the energy accumulators 29 radially. The disk part 25 therebyforms the complete output part 34 of the damper stage 14, whereas thedisk part 25 in the damper stage 15 forms a part of the input parts 35,which is completed by a second disk part 31 with correspondingwindow-shaped recesses 32. The two disk parts 25, 31 are axially spacedrelative to one another by means of the rivets 33 and rigidly connectedand accommodate the flange part 36, which is rigidly connected e.g.welded or formed as one piece with the output hub 12. To ensure therotating ability of the flange part 36, acting as output part 48 of bothdamper stages 14, 15, with respect to the input part 35 of the damperstage 15, circular segment shaped cutouts 49 are provided in the flangepart 36, whereby after consumption of the rotational clearance therivets 33 strike on the cutouts and the torque from the output part 34of the damper stage 14 is transmitted to the flange part 36 and fromthere to the output hub 12.

In radial extension, the disk part 31 in a single-piece manner forms themounting part 37 of the torsional vibration absorber 17, which, throughthis design, forms a centrifugal force pendulum 38, in that on bothsides of the mounting part 37 absorber masses 39 spaced axially apartare distributed over the circumference, which are connected with oneanother by means of rivets 40 and are guided in circumferentialdirection and in radially extending raceways—not visible in detail.Between the rivets 40 and the raceways, a bearing such as plain orroller bearing can be provided. Through the single-piece connection ofthe mounting part 37 with the input part 35 of the damper stage 15 andthe output part 34 of the damper stage 15 by means of the rivets 33 isthe centrifugal force pendulum 38 assigned parallel to both damperstages.

The input part 41 of the damper stage 14 is formed by a ring part 42,which is centered on a centering circumference 43 of the flange part 36and is permanently connected by means of transmission connections 44like rivets with a ring gear 45, which forms a tooth system with anexternal teeth 46 of the friction plate 22. During assembly of bothhousing parts 4, 5, the tooth system is formed between the frictionplate preassembled in the housing part 5 and the ring gear 45preassembled in the housing part 4.

To ensure that the mounting part 37 or disk parts 31 is rotatable,circular segment-shaped openings 47 are provided in said part, throughwhich the transmission connections 44 are guided.

For further reduction of the axial assembly space are energyaccumulators 29 disposed radially outside the turbine 7 and surroundsaid turbine at least partially axially. The energy accumulators 27 arebrought closer to the turbine 7 in the tapered area between turbineblades 8 and the fastening on the disk part 25. The carrier masses 39are closely spaced axially to the energy accumulators 29 radiallydisposed outside the lock-up clutch 13.

The functioning manner of the torsional vibration damper 16 isdifferentiated in the state with actuated and non-actuated lock-upclutch 13. If this is opened then the damper stage 14 is out ofoperation because the input part 41 is essentially without load. Thetorque flows from the turbine 7 into the damper stage 15 via the inputpart 35 and the energy accumulators 27 into the output part 48 as flangepart 36 and from there via the output hub 12 into the transmission inputshaft.

When lock-up clutch 13 is actuated, the torque is introduced via thefrictional plate 22, the gearing and the transmission connections 44 inthe input part 41. The input part 41 pressurizes the energy accumulators29, which can be arc springs, and said transmit the torque afterconsuming the rotary clearance of the cutouts 49 by means of limitstopped rivets 33, the torque to the common output part 48 acting asflange part 36 and from there via the output hub 12 on the transmissioninput shaft. The energy accumulators 27 are preferably designed withstiffness, such that the torque transmitted through said stiffness doesnot lead to consumption of the rotary clearance and torque peaks aredamped through the elastic properties of the energy accumulators.Thereby, the centrifugal force pendulum 38 is active in a particularlyadvantageous manner, so that in the elastic operating range of bothdamper stages 14, 15, they are additionally active in vibration damping.

LIST OF REFERENCE SYMBOLS

-   1 hydrodynamic torque converter-   2 rotation axis-   3 housing-   4 housing part-   5 housing part-   6 impeller-   7 turbine-   8 turbine blade-   9 fastening means-   10 stator-   11 one way clutch-   12 output hub-   13 lock-up clutch-   14 damper stage-   15 damper stage-   16 torsional vibration damper-   17 torsional vibration absorber-   18 piston-   19 leaf spring-   20 chamber-   21 chamber-   22 friction plate-   23 housing wall-   24 pocket-   25 disk part-   26 fastening means-   27 energy accumulator-   28 recess-   29 energy accumulator-   30 formed-part-   31 disk part-   32 recess-   33 rivet-   34 output part-   35 input part-   36 flange part-   37 mounting part-   38 centrifugal force pendulum-   39 absorber mass-   40 rivet-   41 input part-   42 ring part-   43 centering circumference-   44 transmission connection-   45 ring gear-   46 external teeth-   47 opening-   48 output part-   49 cutout

What is claimed is:
 1. A hydrodynamic torque converter (1) with aturbine (7) driven by an impeller (6) as well as housing (3) in which atorsional vibration damper (16) with multiple of damper stages (14, 15),a torsional vibration absorber (17) and a lock-up clutch (13) areadditionally installed, wherein a first damper stage (14) and a seconddamper stage (15) are disposed between the lock-up clutch (13) and anoutput hub (12), the second damper stage (15) is disposed between theturbine (7) and the output hub (12) and the torsional vibration absorber(17) is parallel to both damper stages (14, 15).
 2. The hydrodynamictorque converter (1) according to claim 1, wherein an input part (41) ofthe first damper stage (14) and an output part (48) of the second damperstage (15) are centered on one another.
 3. The hydrodynamic torqueconverter (1) according to claim 1, wherein a disk part (25) isallocated to two damper stages (14, 15) as one piece.
 4. Thehydrodynamic torque converter (1) according to claim 1, wherein thetorsional vibration absorber (17) comprises a plurality of absorbermasses (39), and a mounting part (37) of the torsional vibrationabsorber (17) forms a disk part (31) of an input part (35) of the seconddamper stage (15).
 5. The hydrodynamic torque converter (1) according toclaim 1, wherein absorber masses (39) of the torsional vibrationabsorber (17) and energy accumulators (29) of the first damper stage(14) disposed over the circumference are radially at the same height butaxially spaced apart.
 6. The hydrodynamic torque converter (1) accordingto claim 5, wherein a middle mounting diameter of the energyaccumulators (29) is disposed radially outside the turbine (7).
 7. Thehydrodynamic torque converter (1) according to claim 5, wherein theenergy accumulators (29) overlap the turbine (7) at least partially andaxially.
 8. The hydrodynamic torque converter (1) according to claim 1,wherein energy accumulators (27) are distributed over the circumferenceof the second damper stage (15) based on a middle mounting diameterradially within turbine blades (8) of the turbine (7).
 9. Thehydrodynamic torque converter (1) according to claim 8, wherein theenergy accumulators (27) of the second damper stage (15) and the turbine(7) at least partially and axially overlap.
 10. The hydrodynamic torqueconverter (1) according to claim 1, wherein the lock-up clutch (13) in aclosed state is axially mounted in a pocket (24) formed in a housingwall (23) radially inward of fastening means (9) provided on externalpart of the torque converter (1).
 11. The hydrodynamic torque converter(1) according to claim 10, wherein the lock-up clutch (13) is formed outof a piston (18) centered on the output hub (12) and mountednon-rotatably and axially displacably on the housing (3), and axiallypressurizes a friction plate (22) that can be clamped between saidpiston and said housing (3) to develop a frictional engagement.
 12. Thehydrodynamic torque converter (1) according to claim 11, wherein amounting part (37) of the torsional vibration absorber (17) is disposedaxially between lock-up clutch (13) and the first damper stage (14). 13.The hydrodynamic torque converter (1) according to claim 12, whereinbetween the friction plate (22) and an input part (41) of the firstdamper stage (14) transition connections (44) are formed, which reachthrough circular segment-shaped openings (47) of the mounting part (37).14. The hydrodynamic torque converter according to claim 1, wherein inthe closed state of the lock-up clutch (13) the torsional vibrationabsorber (17) acts between both damper stages (14, 15).
 15. Thehydrodynamic torque converter according to claim 1, wherein thetorsional vibration absorber (17) is connected non-rotatably with theturbine (7).
 16. The hydrodynamic torque converter according to claim15, wherein in the opened state of the lock-up clutch (13) the torsionalvibration absorber (17) is connected non-rotatably with the turbine (7).17. A hydrodynamic torque converter (1) with a turbine (7), driven by animpeller (6), as well as housing (3) in which a torsional vibrationdamper (16) with multiple damper stages (14, 15), a torsional vibrationabsorber (17) and a lock-up clutch (13) are additionally installed,wherein the torsional vibration absorber includes a centrifugal forcependulum, wherein a first damper stage (14) and a second damper stage(15) of the multiple damper stages are disposed between the lock-upclutch (13) and an output hub (12), the second damper stage (15) isdisposed between the turbine (7) and the output hub (12) and thecentrifugal force pendulum is connected to an interconnection between anoutput of the first damper stage and an input of the second damper stageso that the centrifugal force pendulum is parallel to both damper stages(14, 15), wherein the centrifugal force pendulum is connectednon-rotatably relative to the turbine (7) and a disk part that forms theinterconnection between the input part of the second damper stage andthe output part of the first damper stage, wherein the centrifugal forcependulum comprises a plurality of absorber masses (39) and a mountingpart (37), and wherein the mounting part forms part of the disk partwith the input part (35) of the second damper stage (15).
 18. Thehydrodynamic torque converter (1) according to claim 17, wherein thedisk part that connects the first and second damper stages (14, 15) is asingle piece.
 19. The hydrodynamic torque converter (1) according toclaim 17, wherein the torsional vibration damper comprises energyaccumulators (29) for the first damper stage (14), and the absorbermasses and the energy accumulators are disposed over a circumferenceradially at a same height and axially spaced apart.
 20. The hydrodynamictorque converter (1) according to claim 17, wherein the mounting part(37) of the centrifugal force pendulum is disposed axially between thelock-up clutch (13) and the first damper stage (14).
 21. Thehydrodynamic torque converter according to claim 17, wherein in a closedstate of the lock-up clutch (13) torque flows through the first damperstage and the second damper stage such that the centrifugal forcependulum acts on both damper stages (14, 15), and wherein in an openstate of the lockup clutch, torque flows through only the second damperstage such that the centrifugal force pendulum acts only on the seconddamper stage.
 22. The hydrodynamic torque converter according to claim17, wherein a further disk part connected to the disk part forms amounting part of the centrifugal force pendulum.
 23. The hydrodynamictorque converter according to claim 17, wherein the disk part forms atleast an output of the first damper.
 24. The hydrodynamic torqueconverter as recited in claim 17, wherein a limit stop for the seconddamper stage is provided on the disk part.
 25. The hydrodynamic torqueconverter according to claim 17, further comprising a fastener fixing aportion of at least one of the first damper stage and the second damperstage to the turbine, wherein the absorber masses are positionedradially outside of the fastener, and the second damper stage includesenergy accumulators positioned radially outside of the fastener.
 26. Thehydrodynamic torque converter according to claim 17, wherein themultiple damper stages include energy accumulators, the absorber massesextending radially outside of the energy accumulators.
 27. Ahydrodynamic torque converter (1) with a turbine (7) driven by animpeller (6) as well as housing (3) in which a torsional vibrationdamper (16) with multiple of damper stages (14, 15), a torsionalvibration absorber (17) and a lock-up clutch (13) are additionallyinstalled, wherein the torsional vibration absorber is a centrifugalforce pendulum, wherein a first damper stage (14) and a second damperstage (15) of the multiple damper stages are disposed between thelock-up clutch (13) and an output hub (12), the second damper stage (15)is disposed between the turbine (7) and the output hub (12) and thecentrifugal force pendulum is connected to an interconnection between anoutput part of the first damper stage and an input part of the seconddamper stage so that the centrifugal force pendulum is parallel to bothdamper stages (14, 15), the centrifugal force pendulum is connectednon-rotatably relative to the turbine (7) and a disk part that formspart of the interconnection between the output part of the first damperstage and an input part of the second damper stage, and wherein amounting part (37) of the centrifugal force pendulum is disposed axiallybetween the lock-up clutch (13) and the first damper stage (14).
 28. Thehydrodynamic torque converter according to claim 27, wherein themounting part is connected to the disk part and a plurality of absorbermasses movably mounted on the mounting part.
 29. The hydrodynamic torqueconverter according to claim 28, wherein a further disk part forms themounting part.
 30. The hydrodynamic torque converter as recited in claim29 wherein a limit stop for the first damper stage is provided on thefurther disk part.
 31. The hydrodynamic torque converter according toclaim 27, further comprising a fastener fixing a portion of at least oneof the first damper stage and the second damper stage to the turbine,wherein the centrifugal force pendulum comprises masses positionedradially outside of the fastener, and the second damper stage includesenergy accumulators positioned radially outside of the fastener.
 32. Thehydrodynamic torque converter according to claim 27, wherein thecentrifugal force pendulum includes masses and the multiple damperstages include energy accumulators, the masses extending radiallyoutside of the energy accumulators.
 33. The hydrodynamic torqueconverter according to claim 27, wherein a further disk part forms themounting part of the centrifugal force pendulum, and the disk part andthe further disk part together form the input part of the second damperstage.
 34. The hydrodynamic torque converter according to claim 27,wherein the mounting part of the centrifugal force pendulum forms asingle piece with the disk part (31).
 35. The hydrodynamic torqueconverter according to claim 27, wherein the disk part forms an outputpart of the first damper stage, a further disk part forms the mountingpart of the centrifugal force pendulum, and the disk part and thefurther disk part together form an input part of the second damperstage.
 36. The hydrodynamic torque converter according to claim 27,wherein the disk part is a unitary structure.
 37. A hydrodynamic torqueconverter (1) with a turbine (7) driven by an impeller (6) as well ashousing (3) in which a torsional vibration damper (16) with multiple ofdamper stages (14, 15), a torsional vibration absorber (17) and alock-up clutch (13) are additionally installed, wherein the torsionalvibration absorber is a centrifugal force pendulum, wherein a firstdamper stage (14) and a second damper stage (15) of the multiple damperstages are disposed between the lock-up clutch (13) and an output hub(12), the second damper stage (15) is disposed between the turbine (7)and the output hub (12) and the centrifugal force pendulum is connectedto an interconnection between an output of the first damper stage and aninput of the second damper stage so that the centrifugal force pendulumis parallel to both damper stages (14, 15), wherein in a closed state ofthe lock-up clutch (13) torque flows through the first damper stage andthe second damper stage such that the centrifugal force pendulum acts onboth damper stages (14, 15), and wherein in an open state of the lockupclutch, torque flows through only the second damper stage such that thecentrifugal force pendulum acts only on the second damper stage.
 38. Thehydrodynamic torque converter according to claim 37, wherein thetorsional vibration damper includes a unitary disk part that forms theinterconnection between the first damper stage and the second damperstage, and wherein the centrifugal force pendulum includes a mountingpart connected to the disk part and a plurality of absorber massesmovably mounted on the mounting part.
 39. The hydrodynamic torqueconverter according to claim 38, wherein a further disk part forms themounting part.
 40. The hydrodynamic torque converter according to claim38, further comprising a fastener fixing a portion of the first damperstage to the turbine, wherein the plurality of absorber masses arepositioned radially outside of the fastener, and the second damper stageincludes energy accumulators positioned radially outside of thefastener.
 41. The hydrodynamic torque converter according to claim 38,wherein the multiple damper stages include energy accumulators, theabsorber masses extending radially outside of the energy accumulators.42. The hydrodynamic torque converter according to claim 41, wherein thedisk part forms an output part of the first damper stage.
 43. Thehydrodynamic torque converter according to claim 38, wherein themounting part comprises a further disk part, and the disk part and thefurther disk part together form the input part of the second damperstage.
 44. A hydrodynamic torque converter (1) with a turbine (7) drivenby an impeller (6) as well as housing (3) in which a torsional vibrationdamper (16) with multiple of damper stages (14, 15), a torsionalvibration absorber (17) and a lock-up clutch (13) are additionallyinstalled, wherein the torsional vibration absorber is a centrifugalforce pendulum, wherein a first damper stage (14) and a second damperstage (15) of the multiple damper stages are disposed between thelock-up clutch (13) and an output hub (12), the second damper stage (15)is disposed between the turbine (7) and the output hub (12) and thecentrifugal force pendulum is connected to an interconnection between anoutput of the first damper stage and an input of the second damper stageso that the centrifugal force pendulum is parallel to both damper stages(14, 15), wherein a limit stop for the first damper stage is provided ona disk part connected to the centrifugal force pendulum, wherein in aclosed state of the lock-up clutch (13) torque flows through the firstdamper stage and the second damper stage such that the centrifugal forcependulum acts on both damper stages (14, 15), and wherein in an openstate of the lockup clutch, torque flows through only the second damperstage such that the centrifugal force pendulum acts only on the seconddamper stage.
 45. The hydrodynamic torque converter according to claim44, wherein the centrifugal force pendulum includes a mounting partconnected to the interconnection between the first damper stage and thesecond damper stage and a plurality of absorber masses movably mountedon the mounting part.
 46. The hydrodynamic torque converter according toclaim 45, wherein the disk part forms the mounting part.
 47. Thehydrodynamic torque converter according to claim 44, wherein thecentrifugal force pendulum includes masses and the multiple damperstages include energy accumulators, the masses extending radiallyoutside of the energy accumulators.
 48. The hydrodynamic torqueconverter according to claim 44, wherein a mounting part of thecentrifugal force pendulum forms a single piece with the disk part (31).49. The hydrodynamic torque converter according to claim 44, wherein thedisk part is a unitary structure.